CN105937438A - Internal combustion engine - Google Patents
Internal combustion engine Download PDFInfo
- Publication number
- CN105937438A CN105937438A CN201610121368.2A CN201610121368A CN105937438A CN 105937438 A CN105937438 A CN 105937438A CN 201610121368 A CN201610121368 A CN 201610121368A CN 105937438 A CN105937438 A CN 105937438A
- Authority
- CN
- China
- Prior art keywords
- spray orifice
- spray
- injected fuel
- orifice
- extended line
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000002485 combustion reaction Methods 0.000 title claims abstract description 40
- 239000007921 spray Substances 0.000 claims abstract description 464
- 239000000446 fuel Substances 0.000 claims abstract description 199
- 238000002347 injection Methods 0.000 claims abstract description 19
- 239000007924 injection Substances 0.000 claims abstract description 19
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 17
- 238000005507 spraying Methods 0.000 claims description 9
- 239000000463 material Substances 0.000 claims description 7
- 230000000694 effects Effects 0.000 description 9
- 239000003595 mist Substances 0.000 description 4
- 238000010304 firing Methods 0.000 description 3
- 238000001514 detection method Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 230000001629 suppression Effects 0.000 description 2
- PEDCQBHIVMGVHV-UHFFFAOYSA-N Glycerine Chemical compound OCC(O)CO PEDCQBHIVMGVHV-UHFFFAOYSA-N 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000010892 electric spark Methods 0.000 description 1
- 239000003500 flue dust Substances 0.000 description 1
- 238000007689 inspection Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
- F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
- F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
- F02B23/104—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder the injector being placed on a side position of the cylinder
- F02B23/105—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder the injector being placed on a side position of the cylinder the fuel is sprayed directly onto or close to the spark plug
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
- F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
- F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F1/242—Arrangement of spark plugs or injectors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/14—Arrangements of injectors with respect to engines; Mounting of injectors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/162—Means to impart a whirling motion to fuel upstream or near discharging orifices
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
- F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
- F02M61/1813—Discharge orifices having different orientations with respect to valve member direction of movement, e.g. orientations being such that fuel jets emerging from discharge orifices collide with each other
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
- F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
- F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
- F02B2023/103—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder the injector having a multi-hole nozzle for generating multiple sprays
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fuel-Injection Apparatus (AREA)
- Combustion Methods Of Internal-Combustion Engines (AREA)
Abstract
Stable combustion is achieved in an internal combustion engine, in cases where an air stream has occurred in a cylinder. The engine includes a fuel injection valve having a first nozzle hole and a second nozzle hole, and an spark plug disposed at a position through which the swirling flow flows, and which is at the downstream side of the flow of the swirling flow from an extension line of the first nozzle hole and at the upstream side of the flow of the swirling flow from an extension line of the second nozzle hole, for igniting a spray of fuel injected from the fuel injection valve, wherein the first nozzle hole and the second nozzle hole are formed in such a manner that the shortest distance from the extension line of the first nozzle hole to the spark plug becomes longer than the shortest distance from the extension line of the second nozzle hole to the spark plug.
Description
Technical field
The present invention relates to internal combustion engine.
Background technology
Known have a kind of in the way of configuring spark plug between injected fuel spray and injected fuel spray, form fuel
The technology (for example, referring to patent documentation 1) of the spray orifice of injection valve.In the art, so that spark
The fuel concentration of plug periphery becomes the mode of desired value and configures spray orifice.
Prior art literature
Patent documentation
Patent documentation 1: Japanese Unexamined Patent Application Publication 2003-534486 publication
Patent documentation 2: Japanese Unexamined Patent Publication 2011-094604 publication
Summary of the invention
The problem that invention is to be solved
In above-mentioned patent documentation, do not account for the impact of air-flow produced in cylinder, therefore,
In the case of injected fuel spray has been flowed because of air-flow, according to the position relationship of injected fuel spray Yu spark plug,
Likely it is difficult to igniting.Namely, it is possible to due to the fact that and be difficult to igniting: due to combustion
Material spraying is close to spark plug, and when plug ignition, the fuel concentration near spark plug can become too high,
Or, owing to injected fuel spray is away from spark plug, the fuel rich when plug ignition, near spark plug
Degree can become too low.
The present invention is the invention completed in view of problem points as above, it is intended that at cylinder
Stable burning is realized in the case of inside creating air-flow.
Means for solving the above
In order to solve the problems referred to above, a kind of internal combustion engine is provided in the present invention, is whirled up in cylinder
Stream, wherein, described internal combustion engine possesses: Fuelinjection nozzle, and it has and at least includes in described cylinder
First spray orifice of injection fuel and multiple spray orifices of the second spray orifice；And igniter, it is arranged in described
The extended line of the first spray orifice described in ratio in the position that swirling flow flows through is by the flow direction of described swirling flow
Downstream and than the extended line of described second spray orifice by the position of flow direction upstream side of described swirling flow
Putting, the spraying to the fuel ejected from described Fuelinjection nozzle is lighted a fire, described first spray orifice and
Described second spray orifice is formed as from the extended line of the described first spray orifice beeline to described igniter
Longer to the beeline of described igniter than from the extended line of described second spray orifice.
The relative position relation of igniter and Fuelinjection nozzle and spray orifice towards being configured to igniting
The spraying of the fuel flowed because of swirling flow ejected from Fuelinjection nozzle can be carried out a little by device
Fire.In the case of from the point of view of igniter, spray fuel from the first spray orifice to the upstream side of swirling flow,
Spray fuel to the downstream of swirling flow from the second spray orifice.Therefore, from the injected fuel spray of the first spray orifice
Because of swirling flow close to igniter within the period to igniting, on the other hand, from the second spray
The injected fuel spray in hole because of swirling flow to igniting period in away from igniter.Therefore, in advance
Presumably from the injected fuel spray of the first spray orifice because of swirling flow close to the situation of igniter, and by first spray
Hole is formed as making the injected fuel spray from the first spray orifice fill towards the upstream side of swirling flow away from igniting in advance
Put.Equally, it is contemplated that from the injected fuel spray of the second spray orifice because of swirling flow away from the situation of igniter,
And the second spray orifice is formed as making the injected fuel spray from the second spray orifice in advance towards the upstream side of swirling flow
Close to igniter.Its result, from the extended line of the first spray orifice beeline to igniter than from
The extended line of the second spray orifice is long to the beeline of igniter.By so forming the first spray orifice and the
Two spray orifices, when ignition device, the injected fuel spray even if from two spray orifices there occurs flowing, point
Fire device also can become, with the position relationship of injected fuel spray, the relation being suitable to burn, it is possible to realize steady
Fixed burning.
It addition, described first spray orifice and described second spray orifice can be formed as the prolongation of described first spray orifice
The extended line of line and described second spray orifice is the most overlapping on the flow direction of described swirling flow.
Then, injected fuel spray is at least some of the most overlapping on the flow direction of swirling flow.If assuming
The injected fuel spray of the first spray orifice and the injected fuel spray of the second spray orifice are overlapping on the flow direction of swirling flow,
Then the air-flow with the injected fuel spray collision rift of the first spray orifice is difficult to arrive the injected fuel spray of the second spray orifice.Cause
This, the effect of swirling flow diminishes.On the other hand, if making extended line and second spray orifice of the first spray orifice
Extended line the most overlapping on the flow direction of swirling flow, then at least the one of the injected fuel spray of the second spray orifice
Part is directly exposed to air-flow, so also being able to obtain swirling flow in the injected fuel spray of the second spray orifice
Effect.Therefore, it is possible to realize stable burning.
It addition, described first spray orifice and described second spray orifice can be formed as the prolongation of described first spray orifice
The central shaft angulation of line and described Fuelinjection nozzle than the extended line of described second spray orifice with described
The central shaft angulation of Fuelinjection nozzle is big.
Just after the second spray orifice ejects fuel, injected fuel spray is closer from igniter, so from
The fuel that this second spray orifice ejects likely be attached to igniter and hinder after igniting.Relatively
In this, the central shaft angulation of extended line with Fuelinjection nozzle by making the second spray orifice is smaller,
The distance between the injected fuel spray and igniter of the second spray orifice can be made elongated.Therefore, pass through
Make the prolongation than the second spray orifice of the extended line of the first spray orifice and the central shaft angulation of Fuelinjection nozzle
Line is big with the central shaft angulation of Fuelinjection nozzle, it is possible to suppression fuel is attached to igniter,
It is possible to realize stable burning.
It addition, described first spray orifice and described second spray orifice can be formed as from described first spray orifice
Injected fuel spray and the injected fuel spray from described second spray orifice have one on the flow direction of described swirling flow
Half is above the most overlapping.So, more than half of injected fuel spray from the second spray orifice directly exposes
In swirling flow, so the effect of swirling flow becomes much larger.
It addition, described first spray orifice and described second spray orifice can be formed as the prolongation of described first spray orifice
The central shaft angulation of line and described Fuelinjection nozzle than the extended line of described second spray orifice with described
Big more than 5 degree of the central shaft angulation of Fuelinjection nozzle.
Here, from the injected fuel spray of each spray orifice such as with the angular expanse of 10 degree.Therefore, by inciting somebody to action
The central shaft angulation of the extended line of the first spray orifice and Fuelinjection nozzle and the extended line of the second spray orifice
With half that is 5 degree that the difference of the central shaft angulation of Fuelinjection nozzle is set to such as 10 degree, it is possible to
Suppress the injected fuel spray from the first spray orifice and the injected fuel spray from the second spray orifice in the flowing of swirling flow
There is more than half overlapping, so also being able to back in the injected fuel spray from the second spray orifice on direction
The effect of eddy flow.
Furthermore it is possible to by by described first spray orifice from can be by the region of described ignition device
The outer rim of upstream side stagger such as lower angle to the upstream side of described swirling flow, by described second spray orifice
Towards from can be by the outer rim in the downstream in the region of described ignition device to described swirling flow
Upstream side staggers this angle, makes from the shortest to described igniter of the extended line of described first spray orifice
Distance is longer to the beeline of described igniter than the extended line from described second spray orifice, described angle
Be the fuel from described Fuelinjection nozzle be ejected into described igniter igniting period fuel spray
The angle that mist rotates because of described swirling flow.
That is, by make the first spray orifice and the second spray orifice stagger angle that injected fuel spray rotates because of swirling flow,
When ignition device, injected fuel spray is present in ignitable region, it is possible to realize stable combustion
Burn.
It addition, described swirling flow can be to circle round centered by the central shaft of described Fuelinjection nozzle
Eddy current.By this eddy current, the injected fuel spray from the first spray orifice and the spray of the fuel from the second spray orifice
Mist all circles round centered by central axis of air cylinder.Therefore, igniter is closed with the position of injected fuel spray
System changes because of eddy current.Even if in this case, it is also possible to by igniter and Fuelinjection nozzle
Relative position relation and spray orifice towards be set to can be to the injected fuel spray after flowing because of eddy current
Light a fire.Even if additionally, also being able to similarly consider in the case of swirling flow is tumble flow.
Invention effect
According to the present invention, in the case of creating air-flow in cylinder, it is capable of stable burning.
Accompanying drawing explanation
Fig. 1 is the figure of the schematic configuration illustrating the internal combustion engine of embodiment and air intake-exhaust system thereof.
Fig. 2 is that the Fuelinjection nozzle from embodiment 1 is observed in the upside (cylinder head side) from cylinder
The figure of injected fuel spray.
Fig. 3 is the spark plug under the Section A-A illustrating Fig. 2 and the injected fuel spray from Fuelinjection nozzle
The figure of relation.
Fig. 4 be illustrate the air-flow in cylinder intensity, be ejected into from fuel igniting time (injection-
Firing interval) and the figure of relation of offset of the first spray orifice and the second spray orifice.
Fig. 5 is the spark plug under the Section A-A illustrating Fig. 2 and the injected fuel spray from Fuelinjection nozzle
The figure of relation, and be the situation that the spray angle of the spray angle of the first spray orifice and the second spray orifice is equal
Under figure.
Fig. 6 is by the position of the spray orifice of Fuelinjection nozzle with the cross section with the orthogonality of center shaft of Fuelinjection nozzle
Put the figure in the case of cut-out.
Fig. 7 is that the section B-B with Fig. 6 will have first spray orifice corresponding with Fig. 5 and the second spray orifice
The sectional view that Fuelinjection nozzle cuts off.
Fig. 8 is the spark plug under the Section A-A illustrating Fig. 2 and the injected fuel spray from Fuelinjection nozzle
The figure of relation, and be the different situation of the spray angle of the spray angle of the first spray orifice and the second spray orifice
Under figure.
Fig. 9 is that the section B-B with Fig. 6 will have first spray orifice corresponding with Fig. 8 and the second spray orifice
The sectional view that Fuelinjection nozzle cuts off.
Figure 10 is that the spark plug under the Section A-A illustrating Fig. 2 sprays with the fuel from Fuelinjection nozzle
The figure of the relation of mist, and be the feelings making the spray angle of the first spray orifice less than the spray angle of the second spray orifice
Figure under condition.
Figure 11 is that the spark plug under the Section A-A illustrating Fig. 2 sprays with the fuel from Fuelinjection nozzle
The figure of the relation of mist, and be air-flow figure in the case of incline direction collides with injected fuel spray.
Figure 12 is the figure of the injected fuel spray in the case of the observation of the upside of cylinder creates tumble flow.
Label declaration
1: internal combustion engine
2: cylinder
5: spark plug
6: Fuelinjection nozzle
6a: spray orifice
6a1: the first spray orifice
6a2: the second spray orifice
9: inlet valve
10: exhaust valve
20:ECU
610: extended line
611: injected fuel spray
612: injected fuel spray
620: extended line
621: injected fuel spray
622: injected fuel spray
Detailed description of the invention
Hereinafter, referring to the drawings, based on embodiment, detailed description of the invention is described in detail illustratively.
But, about size, material, shape and the relative configuration thereof of the component parts described in the present embodiment
Deng, as long as no particularly recording, just it is not intended to the scope of the present invention is defined.
(embodiment 1)
Fig. 1 is the figure of the schematic configuration illustrating the internal combustion engine of the present embodiment and air intake-exhaust system thereof.Figure
Internal combustion engine 1 shown in 1 is the gasoline engine of 4 strokes possessing multiple cylinder 2.Additionally, at Fig. 1
In, illustrate only 1 cylinder in multiple cylinder.
In each cylinder 2 of internal combustion engine 1, piston 3 is installed in the way of sliding freely.Piston 3
It is linked to not shown output shaft (bent axle) via connecting rod 4.It addition, the inside of cylinder 2 be formed at
The air inlet 7 of cylinder head 11 connects with air vent 8.The opening of the air inlet 7 in cylinder 2 is by entering
Valve 9 carries out opening and closing.The opening of the air vent 8 in cylinder 2 is carried out opening and closing by exhaust valve 10.Enter
Valve 9 and the not shown admission cam of each freedom of exhaust valve 10 and exhaust cam carry out driven for opening and closing.
And then, in cylinder head 11 side of each cylinder 2, be configured with near the central shaft of cylinder 2 for
In this cylinder 2, spray the Fuelinjection nozzle 6 of fuel, and be equipped with from Fuelinjection nozzle 6
The fuel ejected carries out the spark plug 5 lighted a fire.About Fuelinjection nozzle 6, will be described later.
Additionally, in the present embodiment, spark plug 5 is equivalent to the igniter in the present invention.
Air inlet 7 connects with intake channel 70.It is configured with air throttle 71 at intake channel 70.Than
Air throttle 71 intake channel by the upstream 70 is configured with mass air flow sensor 72.Air vent 8 leads to aerofluxus
Road 80 connects.
Further, internal combustion engine 1 and be provided with control this internal combustion engine 1 electronic-controlled installation i.e. ECU
(Electronic Control Unit: electronic control unit) 20.ECU20 and above-mentioned mass air flow sensor
72, crankshaft position sensor 21 and accelerator position sensor 22 electrically connect, the inspection of each sensor
Measured value is delivered to ECU20.ECU20 will appreciate that detected value based on mass air flow sensor 72 obtains
Suction air capacity, detection based on crankshaft position sensor 21 obtain internal combustion engine rotary speed, base
Operating condition in internal combustion engines 1 such as the engine load that the detection of accelerator position sensor 22 obtains.
It addition, ECU20 electrically connects with spark plug 5, Fuelinjection nozzle 6, air throttle 71 etc., these equipment
It is controlled by ECU20 respectively.
Here, Fig. 2 is the upside (cylinder head 11 side) from cylinder 2 observes the combustion from the present embodiment
The figure of the injected fuel spray of material injection valve 6.It addition, Fig. 3 is the spark under the Section A-A illustrating Fig. 2
Fill in the figure of 5 and the relation of the injected fuel spray from Fuelinjection nozzle 6.Section A-A be with from fuel
Injection valve 6 is orthogonal towards the direction of spark plug 5 and carries out cutting off by the plane of spark plug 5 and obtains
The cross section arrived.Additionally, dotted line can also be set to the injected fuel spray after just having sprayed fuel.It addition, 610
The extended line of the first spray orifice 6a1 of one of the spray orifice 6a being denoted as Fuelinjection nozzle 6,611 and 612
Represent the injected fuel spray from this first spray orifice 6a1.And, 620 are denoted as Fuelinjection nozzle 6
The extended line of the second spray orifice 6a2 of one of spray orifice 6a, 621 and 622 represent from this second spray orifice
The injected fuel spray of 6a2.The extended line 610,620 of spray orifice 6a both can be set to the central shaft of spray orifice 6a
Extended line, it is also possible to be set to represent originally from the line in the direction of spray orifice 6a injection fuel.Shown in dotted line
Injected fuel spray 611,621 represent the injected fuel spray not existed in cylinder 2 in the case of swirling flow,
Injected fuel spray 612,622 shown in solid represent exist in cylinder 2 swirling flow and injected fuel spray because of
Injected fuel spray when swirling flow and spark plug 5 after flowing are lighted a fire.Additionally, in figs. 2 and 3,
Although illustrate only the first spray orifice 6a1 and the second spray orifice 6a2 but it also may possess other spray orifices 6a.
In this case, both spray orifice 6a can be configured in the way of (can also being set to angularly) at equal intervals
Around the central shaft of Fuelinjection nozzle 6, it is also possible to unequal interval (can also be set to the most angularly)
Mode be arranged in around the central shaft of Fuelinjection nozzle 6.Fig. 2 shows the arrow such as double dot dash line
As shown in create the situation of clockwise eddy current (swirl).Additionally, the central shaft of cylinder 2,
The central shaft of Fuelinjection nozzle 6 and the central shaft of eddy current are roughly the same, but without strict conformance.Separately
Outward, although the central shaft of cylinder 2 has been set to parallel with the central shaft of Fuelinjection nozzle 6, but has differed
Fixed necessary parallel.
The Fuelinjection nozzle 6 of the present embodiment, it is considered to eddy current and spray orifice 6a is formed as at spark plug 5 point
During fire, spark plug 5 becomes, with the distance of injected fuel spray 612,622, the distance being suitable to light a fire.Now, fire
Flower plug 5 is configured to carry out stratified combustion with the distance of injected fuel spray 612,622 and (can also set
For sprayguided combustion).Additionally, sprayguided combustion refers near the outer rim of injected fuel spray and fuel
Concentration becomes the position of the concentration being suitable to burning and is burnt by spark plug 5 direct-fire.
Here, in injected fuel spray, the closer to its central side, then fuel concentration is the highest, further away from fuel
The center (more by the outside of injected fuel spray) of spraying, then fuel concentration is the lowest.Further, in injected fuel spray
Outer rim near, fuel concentration become be suitable to burning concentration, i.e. be suitable to burning air-fuel ratio.Therefore,
If being formed as flowing because of eddy current when spark plug 5 is lighted a fire by the first spray orifice 6a1 and the second spray orifice 6a2
Injected fuel spray 612,622 outer rim near be positioned near spark plug 5 (following, also referred to as can point
Flame range territory), then it is capable of more reliable igniting.That is, the extended line 610 of the first spray orifice 6a1 and
Extended line 620 angulation of two spray orifice 6a2 is configured to the injected fuel spray after flowing because of eddy current
612,622 be present in can ignition zone.Additionally, the injected fuel spray 612,622 after flowing because of eddy current
It is present in the straight line pair about the center by the center of Fuelinjection nozzle 6 and spark plug 5 in fig. 2
The position claimed.So, symmetrical across spark plug 5 by injected fuel spray 612,622, it is possible to the most right
Two injected fuel spraies 612,622 are lighted a fire, it is possible to realize more reliable igniting.On the other hand,
The extended line 620 of the extended line 610 and the second spray orifice 6a2 of the first spray orifice 6a1 is not in relation to pass through fuel
The straight line at the center of injection valve 6 and the center of spark plug 5 is symmetrical, the extended line 610 of the first spray orifice 6a1
Short distance with the beeline of spark plug 5 extended line 620 than the second spray orifice 6a2 with spark plug 5
From length.Additionally, beeline said here is not the two-dimensional distance in Fig. 2, but have also contemplated that
Distance in the space of the central axis direction of cylinder 2.So, in the present embodiment, spray orifice 6a is made
Stagger the angle rotated in the period fuel spraying being ejected into igniting from fuel.
On the other hand, if the centre of injected fuel spray is near spark plug 5 when spark plug 5 is lighted a fire,
The most aqueous fuel can be attached to spark plug 5, it is possible to is difficult to produce electric spark.Therefore, it is possible to
It is difficult to make fuel combustion.Even if aqueous fuel is not attached to spark plug 5, fuel concentration also can sometimes
Too high and cause being difficult to igniting.If it addition, the injected fuel spray flowed because of eddy current is from spark plug
5 too far, then can become too low due to the fuel concentration of ignition zone or there is not fuel and be difficult to into
Row igniting.In contrast, in the Fuelinjection nozzle 6 of the present embodiment, the injected fuel spray 612 when igniting,
622 be present in can ignition zone, it is possible to realize stable burning.
Additionally, the burning of aforementioned stable can realize in predetermined operation range.Here, spark plug 5
Ignition timing, the speed being ejected into the time of igniting, eddy current from fuel etc. are likely because of internal combustion engine 1
Operating condition and change, accordingly, it is difficult to spray orifice 6a is formed as in whole operation range igniting time
Spark plug 5 all becomes, with the distance of injected fuel spray 612,622, the distance being suitable to light a fire.Therefore, will spray
Hole 6a is formed as in predetermined operation range the distance of spark plug 5 and injected fuel spray when igniting to be become
Be suitable to the distance of igniting.This predetermined operation range such as can be set to carry out being difficult to enter mixed gas
The operation range of the stratified combustion (sprayguided combustion can also be set to) of row igniting.
Here, Fig. 4 show the air-flow in cylinder 2 intensity, be ejected into from fuel igniting time
Between the relation of offset of (injection-firing interval) and the first spray orifice 6a1 and the second spray orifice 6a2
Figure.Offset refers to make spray orifice 6a stagger to the upstream side of eddy current centered by Fuelinjection nozzle 6
Angle, the angle of the injected fuel spray 611 when the injected fuel spray 612 when referring to the igniting in Fig. 2 and injection
Degree (can also be set to the angle of the injected fuel spray 622 when lighting a fire and the injected fuel spray 621 during injection).
In the diagram, " greatly " represents that offset is big, and " little " represents that offset is little.The intensity of air-flow can also
It is set to the rotary speed of eddy current.The intensity of air-flow is the biggest or to be ejected into time of igniting from fuel the longest,
The distance that then injected fuel spray is flowed till fuel is ejected into igniting is the longest, thus makes offset the biggest,
So that penetrating fuel to the more upstream side spray of the direction of rotation of eddy current.That is, at design Fuelinjection nozzle 6
Time, the intensity of the predetermined air-flow in operation range is the biggest, or is ejected into the time of igniting from fuel
The longest, then make centered by the central shaft of Fuelinjection nozzle 6, make the extended line of the first spray orifice 6a1 and
The angle that the upstream side of the direction of rotation extending alignment eddy current of two spray orifice 6a2 staggers is the biggest.Therefore,
Intensity based on the air-flow in predetermined operation range and be ejected into time of igniting from fuel and form
One spray orifice 6a1 and the second spray orifice 6a2.Additionally, the relation shown in Fig. 4 can be by experiment or mould
Plan etc. is obtained.
So, in the Fuelinjection nozzle 6 of the present embodiment, spray orifice 6a1,6a2 are formed as because of eddy current
And the position of the injected fuel spray 612,622 after flowing becomes suitable position.Therefore, design spray orifice
6a1,6a2 also determine spark plug 5 and the extended line of the first spray orifice 6a1 and the prolongation of the second spray orifice 6a2
The relativeness of line, so that the beeline of the extended line of the first spray orifice 6a1 and spark plug 5 is than
The extended line of two spray orifice 6a2 is long with the beeline of spark plug 5.
As mentioned above, according to the present embodiment, owing to considering the shifting of the injected fuel spray caused by eddy current
Dynamic, the first spray orifice 6a1 and the second spray orifice 6a2 is formed as the injected fuel spray when spark plug 5 is lighted a fire and deposits
Be can ignition zone, it is possible to light a fire more reliably.Therefore, by using the present embodiment
Fuelinjection nozzle 6, be such as capable of stable sprayguided combustion.And, it is possible to suppress by
The generation of the flue dust that the deterioration of fired state causes, the discharge of unburned fuel, the reduction etc. of torque.
(embodiment 2)
In embodiment 1, about the prolonging of extended line 610 and the second spray orifice 6a2 of the first spray orifice 6a1
Long line 620 and the central shaft 60 angulation (hereinafter referred to as spray angle) of Fuelinjection nozzle 6,
Do not make stipulations.In the present embodiment, this angle is specified.In the present embodiment, by
One spray orifice 6a1 and the second spray orifice 6a2 is formed as extended line 610 and second spray orifice of the first spray orifice 6a1
The extended line 620 of 6a2 is the most overlapping on the flow direction of swirling flow.
Here, Fig. 5 be spark plug under the Section A-A illustrating Fig. 25 with from Fuelinjection nozzle 6
The figure of relation of injected fuel spray, and be the spray angle R1 and the second spray orifice 6a2 of the first spray orifice 6a1
Spray angle R2 equal in the case of figure.It addition, Fig. 6 with in Fuelinjection nozzle 6
Mandrel orthogonal cross section the position of the spray orifice 6a of Fuelinjection nozzle 6 is cut off in the case of figure.It addition,
Fig. 7 is that the section B-B with Fig. 6 will have the first spray orifice 6a1 corresponding with Fig. 5 and the second spray orifice 6a2
Fuelinjection nozzle 6 cut off sectional view.Arrow in Fig. 5 represents the flow direction of eddy current.At figure
In 5, the injected fuel spray 611,612 of the upstream side being positioned at the flow direction leaning on eddy current than spark plug 5 is
From the injected fuel spray of the first spray orifice 6a1, it is positioned at the downstream of the flow direction leaning on eddy current than spark plug 5
The injected fuel spray 621,622 of side is the injected fuel spray from the second spray orifice 6a2.The injected fuel spray of Fig. 5
In solid line use with the implication identical with Fig. 3 with dotted line.The spray angle R1 of the first spray orifice 6a1
It is extended line 610 and central shaft 60 angulation of Fuelinjection nozzle 6 of the first spray orifice 6a1, is
Represent that the extended line 610 of the first spray orifice 6a1 is from the Fuelinjection nozzle 6 in the direction towards piston 3
The side surface direction (can also be set to horizontal direction) of heart axial cylinder 2 has tilted the angle of which kind of degree.
The spray angle R2 of the second spray orifice 6a2 is extended line 620 and the Fuelinjection nozzle 6 of the second spray orifice 6a2
Central shaft 60 angulation, be that the extended line 620 representing the second spray orifice 6a2 is from towards piston 3
The side surface direction of central axial cylinder 2 of Fuelinjection nozzle 6 in direction (level side can also be set to
To) tilt the angle of which kind of degree.
Equal at the spray angle R2 of the spray angle R1 and the second spray orifice 6a2 of the first spray orifice 6a1
In the case of, as shown in the single dotted broken line of Fig. 5, injected fuel spray cylinder 2 central axis direction (following,
Also referred to as short transverse) on there is no difference.That is, from the first spray orifice 6a1 injected fuel spray 611,
612 and from the second spray orifice 6a2 injected fuel spray 621,622 short transverse position by first spray
The spray angle R2 of the spray angle R1 and the second spray orifice 6a2 of hole 6a1 determines, therefore, if spray
Degree R1, R2 are identical for firing angle, then the position of short transverse does not has difference.Therefore, in the rotation of eddy current
In the case of injected fuel spray from two spray orifice 6a1,6a2 being projected on direction, two injected fuel spraies are overlapping.
Then, the flowing of air-flow is hindered by the injected fuel spray 612 from the first spray orifice 6a1, and air-flow is difficult to
With injected fuel spray 622 direct collision from the second spray orifice 6a2.That is, from the second spray orifice 6a2's
Injected fuel spray 622 is difficult to be exposed to air-flow, so being difficult to obtain the effect of eddy current.
On the other hand, if spray angle R1, R2 are different, then the position of short transverse can produce difference.
Therefore, in the present embodiment, the first spray orifice 6a1 and the second spray orifice 6a2 is formed as the first spray orifice 6a1
Spray angle R1 and the spray angle R2 of the second spray orifice 6a2 different.Fig. 8 illustrates Fig. 2
The figure of spark plug under Section A-A 5 and the relation of the injected fuel spray from Fuelinjection nozzle 6, and be
In the case of the spray angle R2 of the spray angle R1 and the second spray orifice 6a2 of the first spray orifice 6a1 is different
Figure.It addition, Fig. 9 is the section B-B with Fig. 6 will have the first spray orifice 6a1 corresponding with Fig. 8
The sectional view cut off with the Fuelinjection nozzle 6 of the second spray orifice 6a2.
So, due to the injected fuel spray 611,612 from the first spray orifice 6a1 with from the second spray orifice
The position of the short transverse of the injected fuel spray 621,622 of 6a2 is by the spray angle of the first spray orifice 6a1
The spray angle R2 of R1 and the second spray orifice 6a2 determines, so at the spray angle of the first spray orifice 6a1
In the case of the spray angle R2 of R1 and the second spray orifice 6a2 is different, from the first spray orifice 6a1's
Injected fuel spray 612 and short transverse can be produced between the injected fuel spray 622 of the second spray orifice 6a2
Difference D1.Thus, from least some of (the moon of Fig. 8 of injected fuel spray 622 of the second spray orifice 6a2
Shadow part) it is directly exposed to air-flow, so the effect of eddy current becomes much larger.
Additionally, in the present embodiment, by the spray angle R1 and the second spray orifice 6a2 of the first spray orifice 6a1
Spray angle R2 be set to from the first spray orifice 6a1 injected fuel spray 612 with from the second spray orifice
The injected fuel spray 622 of 6a2 has more than half the most overlapping in the direction of rotation of eddy current.That is, by first
The spray angle R2 of the spray angle R1 and the second spray orifice 6a2 of spray orifice 6a1 is set to: will be from
Direction of rotation from the injected fuel spray 612 of one spray orifice 6a1 to eddy current project area with will from second spray
The area that the injected fuel spray 622 of hole 6a2 projects to the direction of rotation of eddy current has more than half the most overlapping.
In this case, in fig. 8, D1 becomes more than the radius of injected fuel spray.So, get by making
From the injected fuel spray 612 of the first spray orifice 6a1 with the injected fuel spray 622 from the second spray orifice 6a2 in whirlpool
There is more than half the most overlapping, in the injected fuel spray 622 from the second spray orifice 6a2 in the direction of rotation of stream
In also be able to provide eddy current effect.Additionally, about make the spray angle R1 of the first spray orifice 6a1 with
Which kind of degree the spray angle R2 of the second spray orifice 6a2 staggers preferably, although according to each injected fuel spray
Expansion scope and change, if but spray angle is staggered such as more than 5 degree, then can suppress fuel
Spraying has more than half overlapping.In this case, it is contemplated that each injected fuel spray from each spray orifice 6a with such as
The scope expansion of 10 degree.Alternatively, it is also possible to the injected fuel spray expansion considered in common Fuelinjection nozzle
Scope, the upper limit of the angle making spray angle stagger is set to such as 25 degree.That is, spray angle
Difference can be set to more than 5 degree and less than 25 degree.
Additionally, make spray angle R1 and the spray angle of the second spray orifice 6a2 of the first spray orifice 6a1
In the case of R2 staggers, it is contemplated that make the spray angle R1 of the first spray orifice 6a1 than the second spray orifice 6a2
Situation big for spray angle R2 and make the spray angle R1 of the first spray orifice 6a1 than the second spray orifice 6a2
Situation little for spray angle R2.Here, make spray angle the biggest, fuel the most in the height direction
Spraying is closer to spark plug 5.Above-mentioned Fig. 8 shows that the spray angle R1 making the first spray orifice 6a1 is than
The situation big for spray angle R2 of two spray orifice 6a2.On the other hand, Figure 10 is the A-A illustrating Fig. 2
The figure of spark plug under cross section 5 and the relation of the injected fuel spray from Fuelinjection nozzle 6, and be to make the
Figure in the case of the spray angle R1 of one spray orifice 6a1 is less than the spray angle R2 of the second spray orifice 6a2.
In the case of fig. 8, from the injected fuel spray 611,612 of the first spray orifice 6a1 and from the second spray orifice
The injected fuel spray 621,622 of 6a2 is compared, and the position of short transverse is higher, in case of fig. 10,
Injected fuel spray 611,612 and the injected fuel spray from the second spray orifice 6a2 from the first spray orifice 6a1
621,622 comparing, the position of short transverse is relatively low.
Even if here, making the spray angle R1 of the first spray orifice 6a1 injection than the second spray orifice 6a2
In the case of angle R2 is little (Figure 10), from the first spray orifice 6a1 injected fuel spray 612 with from
Also the poor D2 of short transverse can be produced between the injected fuel spray 622 of the second spray orifice 6a2.Thus, from
The injected fuel spray 622 of the second spray orifice 6a2 be directly exposed to air-flow at least partially, so eddy current
Effect becomes much larger.But, if making the spray angle R2 of the second spray orifice 6a2 excessive, then at fuel
During injection, the injected fuel spray 621 from the second spray orifice 6a2 is likely collided with spark plug 5.Therefore,
The aqueous fuel ejected from the second spray orifice 6a2 is likely attached to spark plug 5.If aqueous combustion
Material is attached to spark plug 5, it is likely that be difficult to igniting.
On the other hand, the spray angle R1 of the first spray orifice 6a1 injection than the second spray orifice 6a2 is made
In the case of angle R2 is big (Fig. 8), the just injected fuel spray 621 after the second spray orifice 6a2 injection fuel
Compared with the situation shown in Figure 10 farther from spark plug 5.Therefore, it is possible to suppression is from the second spray orifice 6a2
The fuel ejected is attached to spark plug 5.In embodiment 1, although consider the combustion caused by eddy current
The movement of material spraying, is formed as the igniting at spark plug 5 by the first spray orifice 6a1 and the second spray orifice 6a2
Time injected fuel spray be positioned at ignitable position, if but consider spray angle the most as in this embodiment,
Then it is capable of more stable burning.
Additionally, in the present embodiment, although to the eddy current created centered by the central shaft of cylinder 2
Situation be illustrated, but there is also the central shaft of the eddy current inclined relative to cylinder 2
Situation.That is, there is also air-flow from horizontal direction but not collide with injected fuel spray from incline direction
Situation.Figure 11 be spark plug under the Section A-A illustrating Fig. 25 with from Fuelinjection nozzle 6
The figure of the relation of injected fuel spray, and be air-flow figure in the case of incline direction collides with injected fuel spray.
Even if in this case, by making injected fuel spray 612,622 have one on the flow direction of air-flow
Half is above the most overlapping, it is also possible to makes air-flow straight with a part for the injected fuel spray from the second spray orifice 6a2
Connect collision.
As mentioned above, according to the present embodiment, by making the spray angle R1 of the first spray orifice 6a1
Staggering with the spray angle R2 of the second spray orifice 6a2, the injected fuel spray from the second spray orifice 6a2 exposes
In more air-flow.Therefore, it is possible to the injected fuel spray 612,622 from two spray orifices when reducing igniting
The difference of state.Therefore, it is possible to make to be all formed as wishing from the injected fuel spray 612,622 of two spray orifices
State.Thereby, it is possible to realize stable burning.And then, by making the injection of the first spray orifice 6a1
Angle R1 is bigger than the spray angle R2 of the second spray orifice 6a2, it is possible to suppress from the second spray orifice 6a2 injection
The fuel gone out is attached to spark plug 5, it is possible to realize more reliable igniting.
(embodiment 3)
In the above-described embodiments, the situation creating eddy current as swirling flow is illustrated, and
In the present embodiment, the situation creating tumble flow as swirling flow is illustrated.Tumble flow (tumble)
It it is the swirling flow pivoted about with the axle with the orthogonality of center shaft of cylinder 2.Figure 12 is from cylinder
The upside observation of 2 creates the figure of the injected fuel spray in the case of tumble flow.Figure 12 shows and sprays at fuel
Penetrate the vicinity of valve 6 and spark plug 5 to create towards exhaust valve 10 side from inlet valve 9 side and caused by tumble flow
The situation (with reference to double dot dash line) of air-flow.It addition, spark plug 5 and Fuelinjection nozzle 6 are configured to
Arrange on the direction orthogonal with convolution direction.That is, spark plug 5 and Fuelinjection nozzle 6 is configured to and rolling
The central shaft of stream is arranged in parallel.Further, the first spray orifice 6a1 be formed towards than spark plug 5 lean on into
The direction opening of valve 9 side, the second spray orifice 6a2 is formed towards than spark plug 5 by exhaust valve 10
The direction opening of side.
Then, the injected fuel spray 612 from the first spray orifice 6a1 is flowed because of tumble flow, close to spark plug
5.On the other hand, the injected fuel spray 622 from the second spray orifice 6a2 is flowed because of tumble flow, away from spark
Plug 5.Therefore, each spray orifice 6a is formed as being arranged at the prolongation of the first spray orifice 6a1 of inlet valve 9 side
The prolongation than the second spray orifice 6a2 being arranged at exhaust valve 10 side of the beeline of line 610 and spark plug 5
Line 620 is long with the beeline of spark plug 5.Thus, even if injected fuel spray is flowed because of tumble flow, by
It is positioned at the ignitable scope of spark plug 5, so also being able to more reliable in each injected fuel spray 612,622
Fuel is lighted a fire by ground.
In the case of tumble flow, also as the situation of eddy current, each spray orifice 6a1,6a2 are formed as
The injected fuel spray 612 when spark plug 5 is lighted a fire in the predetermined operation range of enforcement sprayguided combustion,
622 are positioned near spark plug 5.
Even if it addition, in the case of swirling flow is tumble flow, the most similarly to Example 2, by making
The spray angle R1 of one spray orifice 6a1 is bigger than the spray angle R2 of the second spray orifice 6a2, it is possible to suppress from
The fuel that second spray orifice 6a2 ejects is attached to spark plug 5.
As mentioned above, according to the present embodiment, even if in the case of producing tumble flow, it is also possible to real
The most stable burning.
Claims (7)
1. an internal combustion engine, is whirled up flowing in cylinder, wherein,
Described internal combustion engine possesses:
Fuelinjection nozzle, it has the first spray orifice at least included to described vapour cylinder injection fuel and
Multiple spray orifices of two spray orifices；With
Igniter, prolonging of the first spray orifice described in its ratio being arranged in the position that described swirling flow flows through
The long line flow direction downstream by described swirling flow and the extended line than described second spray orifice are by described time
The position of the flow direction upstream side of eddy flow, the spraying to the fuel ejected from described Fuelinjection nozzle
Light a fire,
Described first spray orifice and described second spray orifice are formed as from the extended line of described first spray orifice to described
The beeline of igniter is than the short distance from the extended line of described second spray orifice to described igniter
From length.
Internal combustion engine the most according to claim 1,
Described first spray orifice and described second spray orifice are formed as the extended line and described of described first spray orifice
The extended line of two spray orifices is the most overlapping on the flow direction of described swirling flow.
Internal combustion engine the most according to claim 2,
Described first spray orifice and described second spray orifice are formed as the extended line of described first spray orifice and described combustion
The central shaft angulation of material injection valve is than extended line and the described Fuelinjection nozzle of described second spray orifice
Central shaft angulation big.
4. according to the internal combustion engine described in Claims 2 or 3,
Described first spray orifice and described second spray orifice be formed as from described first spray orifice injected fuel spray and
Injected fuel spray from described second spray orifice has more than half not weigh on the flow direction of described swirling flow
Folded.
Internal combustion engine the most according to claim 4,
Described first spray orifice and described second spray orifice are formed as the extended line of described first spray orifice and described combustion
The central shaft angulation of material injection valve is than extended line and the described Fuelinjection nozzle of described second spray orifice
Big more than 5 degree of central shaft angulation.
6. according to the internal combustion engine according to any one of Claims 1 to 5,
By by described first spray orifice from can be by the upstream side the region of described ignition device
Outer rim staggers such as lower angle to the upstream side of described swirling flow, and by described second spray orifice towards from energy
Enough wrong to the upstream side of described swirling flow by the outer rim in the downstream in the region of described ignition device
Open this angle, make from the extended line of the described first spray orifice beeline to described igniter than from
The extended line of described second spray orifice is long to the beeline of described igniter, and described angle is from institute
The period fuel of the igniting that the fuel stating Fuelinjection nozzle is ejected into described igniter is sprayed because of described
Swirling flow and the angle that rotates.
7. according to the internal combustion engine according to any one of claim 1～6,
Described swirling flow is the eddy current carrying out circling round centered by the central shaft of described Fuelinjection nozzle.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2015042682A JP6217670B2 (en) | 2015-03-04 | 2015-03-04 | Internal combustion engine |
| JP2015-042682 | 2015-03-04 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN105937438A true CN105937438A (en) | 2016-09-14 |
| CN105937438B CN105937438B (en) | 2018-09-28 |
Family
ID=55696840
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610121368.2A Expired - Fee Related CN105937438B (en) | 2015-03-04 | 2016-03-03 | Internal combustion engine |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US10208654B2 (en) |
| EP (1) | EP3064761B1 (en) |
| JP (1) | JP6217670B2 (en) |
| CN (1) | CN105937438B (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108167101A (en) * | 2017-12-28 | 2018-06-15 | 沈阳航空航天大学 | A kind of air-fuel mixture quality optimization method of diesel engine |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3376019B1 (en) * | 2015-11-10 | 2023-01-04 | Nissan Motor Co., Ltd. | Method for controlling internal combustion engine |
| FR3071879B1 (en) * | 2017-09-29 | 2022-03-11 | Ifp Energies Now | TWO-VALVE INTERNAL COMBUSTION ENGINE |
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| CN103967673A (en) * | 2013-02-01 | 2014-08-06 | 马自达汽车株式会社 | Diesel engine |
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| US4974565A (en) * | 1988-02-26 | 1990-12-04 | Toyota Jidosha Kabushiki Kaisha | Fuel swirl generation type fuel injection valve and direct fuel injection type spark ignition internal combustion engine mounted with the fuel injection valve |
| JP2819702B2 (en) * | 1989-12-12 | 1998-11-05 | 株式会社デンソー | Fuel injection valve |
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| JP2002364366A (en) * | 2001-06-11 | 2002-12-18 | Toyota Motor Corp | Combustion chamber for diesel engine and structure of injection nozzle |
| WO2003029635A1 (en) * | 2001-09-17 | 2003-04-10 | Nissan Motor Co., Ltd. | Device and method for forming stratified air-fuel mixture of internal combustion engine |
| US6739309B2 (en) | 2002-06-04 | 2004-05-25 | Nissan Motor Co., Ltd. | Direct fuel injection internal combustion engine |
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| WO2014188736A1 (en) * | 2013-05-20 | 2014-11-27 | 日産自動車株式会社 | Direct injection diesel engine |
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- 2016-02-24 EP EP16157037.9A patent/EP3064761B1/en not_active Not-in-force
- 2016-03-02 US US15/058,250 patent/US10208654B2/en not_active Expired - Fee Related
- 2016-03-03 CN CN201610121368.2A patent/CN105937438B/en not_active Expired - Fee Related
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| JP2003534486A (en) * | 2000-05-26 | 2003-11-18 | ローベルト ボツシユ ゲゼルシヤフト ミツト ベシユレンクテル ハフツング | Fuel injection system and injection method |
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Also Published As
| Publication number | Publication date |
|---|---|
| US10208654B2 (en) | 2019-02-19 |
| JP6217670B2 (en) | 2017-10-25 |
| EP3064761A1 (en) | 2016-09-07 |
| CN105937438B (en) | 2018-09-28 |
| JP2016160894A (en) | 2016-09-05 |
| EP3064761B1 (en) | 2017-10-11 |
| US20160258346A1 (en) | 2016-09-08 |
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